EP1402202A1 - Speed transmission apparatus - Google Patents

Speed transmission apparatus

Info

Publication number
EP1402202A1
EP1402202A1 EP02748476A EP02748476A EP1402202A1 EP 1402202 A1 EP1402202 A1 EP 1402202A1 EP 02748476 A EP02748476 A EP 02748476A EP 02748476 A EP02748476 A EP 02748476A EP 1402202 A1 EP1402202 A1 EP 1402202A1
Authority
EP
European Patent Office
Prior art keywords
rotation
shaft
input
rotate
gear train
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP02748476A
Other languages
German (de)
French (fr)
Inventor
Charles Louis Dupriez
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Individual
Original Assignee
Individual
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Individual filed Critical Individual
Publication of EP1402202A1 publication Critical patent/EP1402202A1/en
Withdrawn legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/72—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
    • F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
    • F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
    • F16H37/10—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing at both ends of intermediate shafts
    • F16H2037/103—Power split variators with each end of the CVT connected or connectable to a Ravigneaux set
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
    • F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
    • F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
    • F16H37/10—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing at both ends of intermediate shafts
    • F16H2037/104—Power split variators with one end of the CVT connected or connectable to two or more differentials
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/46—Gearings having only two central gears, connected by orbital gears
    • F16H3/48—Gearings having only two central gears, connected by orbital gears with single orbital gears or pairs of rigidly-connected orbital gears
    • F16H3/52—Gearings having only two central gears, connected by orbital gears with single orbital gears or pairs of rigidly-connected orbital gears comprising orbital spur gears
    • F16H3/56—Gearings having only two central gears, connected by orbital gears with single orbital gears or pairs of rigidly-connected orbital gears comprising orbital spur gears both central gears being sun gears
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/72—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously
    • F16H3/727—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously with at least two dynamo electric machines for creating an electric power path inside the gearing, e.g. using generator and motor for a variable power torque path

Definitions

  • the present invention relates to a gear transmission device, arranged between a driving motor and a driving receiving device, for example a driving machine, industrial or agricultural, or even the wheels of a motor vehicle.
  • the object of the present invention is to develop a speed transmission apparatus making it possible to modify the transmission ratio without discontinuity, between two determined selectable limits, and without power limitation.
  • the transmission device can be controlled manually or fully automatically, or by combining the two modes.
  • a gear transmission device arranged between a drive motor and a drivable receiving device, comprising a first rotary casing arranged so as to be able to rotate around a first axis of rotation, a double planetary gear train which comprises a first train and a second train and which is arranged at least partially in said first rotary casing, between a drive input connected to the drive motor and an output shaft, arranged so as to be able to rotate around a second axis of rotation and connected to the drive receiving device, the aforementioned double train establishing between the drive input and the output shaft a transmission ratio between an input rotation speed and a output rotation speed, a first rotation transmission arranged at an intermediate output of the first planetary gear train, one two ith rotation transmission arranged at an intermediate input of the second planetary gear train, a first intermediate shaft arranged in one of said first and second rotation transmission, so as to be able to rotate around a third axis of rotation, a first electric motor brake acting
  • the limits are a maximum output speed when the engine brake completely blocks the intermediate shaft and the drive motor is at its maximum power and a zero output speed when the input speed is zero.
  • the speed variation range therefore only depends on the transmission ratio preset by the double planetary gear train chosen and on the application under given conditions, on the one hand, of the appropriate input speed and, on the other hand part, of the engine brake on the intermediate shaft to obtain the appropriate output speed, which can be positive or negative with respect to the drive motor.
  • the apparatus further comprises a second intermediate shaft arranged in the other of said first and second rotation transmissions, so as to be able to rotate around a fourth axis of rotation, and a second electric motor brake, which acts on the second intermediate shaft, being capable of modifying a speed of rotation thereof, following commands received from the control means to which it is electrically connected.
  • the first intermediate shaft and the second intermediate shaft have, in the absence of the engine brakes, different rotation speeds
  • the engine brake acting on the fastest intermediate shaft is an alternator having coils, which excitation is varied to obtain a variable brake effect, and producing an electric current
  • the engine brake acting on the slowest intermediate shaft is an electric motor, which is supplied by the electric current produced by said alternator and which provides a variable acceleration effect.
  • the continuous variation of the engine brake effect is obtained by varying the excitation of the alternator coils, this variation being produced by means of the control means, either manually or by a computer which will take into account different data, such as the speed of the output shaft, the speed of rotation at the input, the requested transmission power, in a similar way to what happens in an automatic gearbox.
  • the control means will now act continuously and not by jumps from certain limits.
  • the first planetary gear train comprises an input shaft arranged at least partially in the first rotary casing so as to be able to rotate around the first axis of rotation and this input shaft is connected to the drive motor and serves as a motor input.
  • the device comprises a second rotary casing, which is arranged so as to be able to rotate around a fifth axis of rotation and in which is housed the second planetary gear train of said double train, which allows a rotation transmission to the output shaft, the first gear train being housed in the first rotary casing.
  • the double planetary gear train is divided into two separate trains, each of which is housed in a clean rotating housing.
  • the first rotary casing is arranged so as to be driven in rotation by the drive motor, thus serving as the motor input of the device, and the double gear train is housed in the first rotary housing.
  • the double gear train is enclosed in a single enclosure and the device is relatively compact.
  • FIG. 1 shows a schematic embodiment, partially in section, of an apparatus according to the invention.
  • FIG. 2 schematically represents another embodiment of the apparatus according to the invention.
  • the transmission device shown is arranged between a current drive motor, not shown, and coupled to an input shaft 1, and a current drivable receiving device, not shown, and coupled to a drive shaft exit 2.
  • the apparatus comprises a double planetary gear train which has a first planetary gear train housed in a first rotary casing 3 and a second planetary gear train housed in a second rotary casing 4.
  • Each rotary casing, with its train of gears, is a known system that can be found on the market for example under the name of the REDEX epicyclic system (firm TEXROPE, cios Industrielle de Transmissions).
  • the first gear train comprises a first planetary carrier plate 5, mounted on the input shaft 1 so as to rotate with it, about its axis of rotation 6, and a second planetary carrier plate 7, mounted on an intermediate output shaft 8 so as to be able to rotate with it, around this same axis of rotation 6.
  • the input shaft 1 partially protrudes from the casing 3, which is coaxial with it, and this so as to be able to rotate freely relative to the casing.
  • this input shaft 1 is hollow and serves as a guide centered on the intermediate output shaft 8, which is also coaxial with the input shaft, and also partially protruding from the casing 3, so to be able to rotate freely in relation to it.
  • pivot axes 9 are supported parallel to the axis of rotation 6, so as to be able to rotate freely on themselves, but so as to be driven in revolution around the axis of rotation 6, when the casing 3 rotates.
  • Each pivot axis 9 carries two satellites 10 and 11 so that they rotate together with this pivot axis.
  • Each satellite 10 and 11 is engaged with one of the planetary carrier plates 5 and 7.
  • the rotary casing 3 finally has a engagement system, for example an external toothing 12 shown diagrammatically, which can engage with a transmission of external rotation.
  • the diameters of the casing 3, of the planetary carrier plates 5 and 7, and of the satellites 10 and 11 are chosen so as to establish between the input shaft 1 and the intermediate output shaft 8 a preselected transmission ratio (which may be modified according to the invention as described below).
  • the second gear train comprises a third planetary carrier plate 13, mounted on an intermediate input shaft 14, so as to rotate around its axis of rotation. In the illustrated embodiment, this axis of rotation is coaxial with the axis of rotation 6.
  • the second gear train further comprises a fourth planetary carrier plate 15 mounted on the output shaft 2 so as to be able to turn with it, this output shaft being again in the example of the Figure 1 coaxial with the axis of rotation 6 and partially projecting from the casing 4.
  • the output shaft 2 is arranged so that it can rotate freely relative to the casing 4 and, in this example, it is provided hollow to serve as a guide centered on the intermediate input shaft 14, which also protrudes partially therefrom out of the casing 4, so that it can rotate freely relative to it.
  • pivot axes 16 are supported parallel to the axis of rotation 6, so as to be able to rotate freely on themselves, but so as to be driven in revolution around the axis of rotation 6, when the casing 4 rotates.
  • Each pivot axis 16 carries two satellites 17 and 18 so that they rotate together with this pivot axis 16.
  • Each of the satellites 17 and 18 is engaged with one of the planetary carrier plates 13 and 15.
  • the rotary casing 4 has an engagement system, for example an external toothing 19 shown diagrammatically, which can engage with an external rotation transmission.
  • the diameters of the casing 4, of the planetary carrier plates 13 and 15 and of the satellites 17 and 18 are chosen so as to establish between the intermediate input shaft 14 and the output shaft 2 a preselected transmission ratio (which may be modified according to the invention as described below).
  • the double planetary gear train illustrated must be chosen so as to establish a given transmission ratio between the input rotation speed and the output rotation speed.
  • a first intermediate shaft 20 is arranged parallel to the axis of rotation 6, so as to be able to rotate on itself. He wears two toothed gears 21 and 22 which are each capable, by a gear, of engaging with the toothing 12 of the casing 3 and respectively the toothing 19 of the casing 4. This arrangement thus produces a first rotation transmission at an intermediate output of the casing 3, transmission which is also engaged with the casing 4.
  • the intermediate output shaft 8 and the intermediate input shaft 14 together form, or provide between them coaxially, an intermediate shaft 23 which thus performs a second rotation transmission between the first planetary gear train and the second, at an intermediate entrance to it.
  • a first engine brake 24 is arranged so as to be able to act on the first intermediate shaft 20.
  • This engine brake can for example be a current alternator, provided with coils, which is electrically connected to a control center 25, for example a computer which integrates input data, such as the power of the drive motor, the rotation speed of the input shaft, the speed of the output shaft, etc. and which can act automatically on the motor brake 24 so that the latter releases the intermediate shaft 20, either the brake, or even possibly blocks it, by varying the excitation of the coils.
  • the energy released is transformed by the alternator into electric current.
  • a second motor brake 26 can also be arranged so as to be able to act on the second intermediate shaft 23, for example by means of toothed gears shown schematically.
  • This second motor brake can for example be an electric motor which is electrically connected to the control center 25, as well as to the first motor brake 24, in order to be able to be supplied with current at least partially by the latter.
  • the control center 25 can act automatically on the engine brake 26 so that the latter releases the intermediate shaft 23, either the brake, or the blocks, by varying the current supply to the electric motor. This recovers the energy released by the first engine brake.
  • This arrangement thus makes it possible to separate on two different axes (the two intermediate shafts) a single input speed, and this by means of the first gear train, which thus forms a first differential, to create an interaction between these two axes, by means of at least one of the engine brakes, before remixing the two gears in the second gear train, which thus forms a second differential.
  • This interaction makes it possible to continuously vary the ratio between the input speed and the output speed. This effect is obtained in particular because the speeds at the outputs of a differential change relative to each other as a function of the resisting torque.
  • ⁇ represents the speed of rotation of the element indicated in subscript
  • d represents the diameter of the element indicated in subscript.
  • a speed of exit ⁇ 2 which can vary between 16 times the speed of entry ⁇ , and -8 / 7 times the speed of entry ⁇
  • the first case corresponds to a forward drive and the second case to a reverse.
  • the intermediate shaft 20 is blocked by the engine brake 24 and the intermediate shaft 23 is free.
  • the intermediate shaft 23 is blocked by the engine brake 26 and the intermediate shaft 20 is released and rotates in the opposite direction. The variation between these two limits is continuous by the set of engine brakes which act on the intermediate shafts.
  • the axes of rotation of the casing 3, of the casing 4, of the input shaft 1, of the output shaft 2, of the intermediate output shaft 8 and the intermediate input shaft 14 are coaxial, it is possible to provide that some of them are not. It is possible for example that the rotation transmission between the intermediate output shaft 8 and the intermediate input shaft 14 form one or more return angles. The same is true for the transmission of rotation between the housing 3 and the housing 4.
  • the rotary casing 27 is unique and the double planetary gear train is completely housed inside it. It is with the rotary housing
  • the rotary casing therefore serves here as a drive input.
  • the double gear train consists of two trains merged into each other.
  • the first gear train comprises a planetary carrier plate 29 mounted on an output intermediate shaft 30, so as to rotate with it, a central plate 31 mounted on the output shaft 32 so as to rotate with it and satellites 33 and 34 arranged between the planetary carrier plate 29 and respectively the central plate 31, on several pivot axes 41 parallel to the axis of rotation 6 of the casing.
  • the satellites are driven in revolution around this axis when the casing 27 rotates.
  • Each pivot axis 41 carries two satellites 33 and 34 which are each engaged with the planetary carrier plate 29 or the central plate 31.
  • the second gear train comprises a planetary carrier plate 35, mounted on an intermediate input shaft 36, so as to rotate about its axis of rotation, and the central plate 31 described above. It also includes satellites, satellite 37 and satellite 34 described above. The satellites 37 are each arranged, like the satellites 33 and 34, on a pivot axis 41.
  • the first rotation transmission comprises the intermediate output shaft 30 as the first intermediate shaft on which the engine brake 38 acts by a set of gears.
  • the second rotation transmission comprises the intermediate input shaft 36 as the second intermediate shaft on which the engine brake 39 acts.
  • the two engine brakes are electrically connected to the control center 40 and to each other.
  • the axes of rotation of the casing 27, the output shaft 32, the intermediate output shaft 30 and the intermediate input shaft 36, are coaxial.
  • This embodiment has the advantage of less bulk.
  • the advantages of the transmission devices according to the invention are inter alia the following: - they make it possible to run any motor permanently at its best efficiency for the requested power, which leads to minimum consumption,
  • the efficiency of the transmission device itself is very high and comparable to that of existing mechanical gearboxes, the transmission of power from the drive motor to the drive receiver device being done by means of gears as in the case of the boxes. mechanical speeds.

Abstract

The invention concerns a speed transmission apparatus, comprising a first rotary crankcase (3), a double planetary gearset, a first rotation transmission (12, 20, 21) arranged at an intermediate output of the first gearset, a second rotation transmission (14) arranged at an intermediate input of the second gearset, a first intermediate shaft (20) arranged in one of said first and second transmission, a first electric compression brake (24) acting on the first intermediate shaft (20) and capable of modifying a rotational speed thereof, and drive means (25) electrically connected to the first compression brake (24), an electrical connection capable of being provided between the first compression brake (24) and a second compression brake (26) whereof the effect is to accelerate the second intermediate shaft (23) by the braking effect exerted on the first intermediate shaft (20) by the compression brake, the energy released by the compression brake (24) being thus recovered by the compression brake (26) and transmitted by the latter to a second intermediate shaft (23).

Description

"Appareil de transmission de vitesses." "Gear transmission apparatus."
La présente invention est relative à un appareil de transmission de vitesses, agencé entre un moteur d'entraînement et un dispositif récepteur entraînable, par exemple une machine à entraîner, industrielle ou agricole, ou bien encore des roues d'un véhicule automobile.The present invention relates to a gear transmission device, arranged between a driving motor and a driving receiving device, for example a driving machine, industrial or agricultural, or even the wheels of a motor vehicle.
Actuellement, cette transmission se fait par l'intermédiaire d'une boîte de vitesses pourvue d'un nombre défini de rapports. L'inconvénient de ce type de transmission est sa discontinuité. Elle ne peut se faire que par sauts successifs.Currently, this transmission is via a gearbox with a defined number of reports. The disadvantage of this type of transmission is its discontinuity. It can only be done by successive jumps.
Pour tenter de remédier à ce problème, on a déjà prévu, dans le cas de moteurs à puissances faibles ou moyennes, des dispositifs de transmission, appelés des variateurs continus, qui ne sont toutefois pas utilisables pour de fortes puissances, supérieures à ± 40 CV (29.420 W).In an attempt to remedy this problem, provision has already been made, in the case of motors with low or medium powers, for transmission devices, called continuous variators, which, however, cannot be used for high powers, greater than ± 40 CV. (29.420 W).
Pour les moteurs à puissances supérieures, on a prévu l'utilisation de boîtes de vitesses automatiques qui permettent d'éviter les interventions manuelles pour changer de rapport de transmission, mais la discontinuité précitée subsiste. La présente invention a pour but de mettre au point un appareil de transmission de vitesses permettant de modifier le rapport de transmission sans discontinuité, entre deux limites déterminées sélectionnables, et sans limitation de puissance. Avantageusement l'appareil de transmission pourra être commandé manuellement ou de façon entièrement automatique, ou en combinant les deux modes. Pour résoudre ces problèmes, on a prévu, suivant l'invention, un appareil de transmission de vitesses, agencé entre un moteur d'entraînement et un dispositif récepteur entraînable, comprenant un premier carter rotatif agencé de manière à pouvoir tourner autour d'un premier axe de rotation, un double train d'engrenages épicycloïdal qui comprend un premier train et un deuxième train et qui est agencé au moins partiellement dans ledit premier carter rotatif, entre une entrée motrice reliée au moteur d'entraînement et un arbre de sortie, agencé de manière à pouvoir tourner autour d'un deuxième axe de rotation et relié au dispositif récepteur entraînable, le double train susdit établissant entre l'entrée motrice et l'arbre de sortie un rapport de transmission entre une vitesse de rotation d'entrée et une vitesse de rotation de sortie, une première transmission de rotation agencée à une sortie intermédiaire du premier train d'engrenages épicycloïdal, une deuxième transmission de rotation agencée à une entrée intermédiaire du deuxième train d'engrenages épicycloïdal, un premier arbre intermédiaire agencé dans l'une desdites première et deuxième transmission de rotation, de manière à pouvoir tourner autour d'un troisième axe de rotation, un premier frein moteur électrique agissant sur le premier arbre intermédiaire et capable de modifier une vitesse de rotation de celui-ci, et des moyens de commande électriquement connectés au premier frein moteur et commandant celui-ci de façon à pouvoir modifier de manière continue la vitesse de rotation du premier arbre intermédiaire et donc le rapport de transmission entre ladite vitesse de rotation d'entrée et ladite vitesse de rotation de sortie.For engines with higher powers, provision has been made for the use of automatic gearboxes which make it possible to avoid manual interventions to change the transmission ratio, but the abovementioned discontinuity remains. The object of the present invention is to develop a speed transmission apparatus making it possible to modify the transmission ratio without discontinuity, between two determined selectable limits, and without power limitation. Advantageously, the transmission device can be controlled manually or fully automatically, or by combining the two modes. To solve these problems, there is provided, according to the invention, a gear transmission device, arranged between a drive motor and a drivable receiving device, comprising a first rotary casing arranged so as to be able to rotate around a first axis of rotation, a double planetary gear train which comprises a first train and a second train and which is arranged at least partially in said first rotary casing, between a drive input connected to the drive motor and an output shaft, arranged so as to be able to rotate around a second axis of rotation and connected to the drive receiving device, the aforementioned double train establishing between the drive input and the output shaft a transmission ratio between an input rotation speed and a output rotation speed, a first rotation transmission arranged at an intermediate output of the first planetary gear train, one two ith rotation transmission arranged at an intermediate input of the second planetary gear train, a first intermediate shaft arranged in one of said first and second rotation transmission, so as to be able to rotate around a third axis of rotation, a first electric motor brake acting on the first intermediate shaft and capable of modifying a speed of rotation thereof, and control means electrically connected to the first motor brake and controlling it so as to be able to continuously modify the speed of rotation of the first intermediate shaft and therefore the transmission ratio between said input rotation speed and said output rotation speed.
On peut ainsi prévoir une variation de vitesse continue entre deux limites théoriques, lorsque le moteur d'entraînement tourne dans un sens donné (marche avant ou marche arrière). Les limites sont une vitesse de sortie maximale lorsque le frein moteur bloque complètement l'arbre intermédiaire et que le moteur d'entraînement est à sa puissance maximum et une vitesse de sortie nulle lorsque la vitesse d'entrée est nulle. La plage de variation de vitesse dépend donc uniquement du rapport de transmission préétabli par le double train d'engrenages épicycloïdal choisi et de l'application dans des conditions données, d'une part, de la vitesse d'entrée appropriée et, d'autre part, du frein moteur sur l'arbre intermédiaire pour obtenir la vitesse de sortie appropriée, celle-ci pouvant être positive ou négative par rapport au moteur d'entraînement.It is thus possible to provide for a continuous speed variation between two theoretical limits, when the drive motor rotates in a given direction (forward or reverse). The limits are a maximum output speed when the engine brake completely blocks the intermediate shaft and the drive motor is at its maximum power and a zero output speed when the input speed is zero. The speed variation range therefore only depends on the transmission ratio preset by the double planetary gear train chosen and on the application under given conditions, on the one hand, of the appropriate input speed and, on the other hand part, of the engine brake on the intermediate shaft to obtain the appropriate output speed, which can be positive or negative with respect to the drive motor.
Suivant une forme de réalisation de l'invention, l'appareil comprend en outre un deuxième arbre intermédiaire agencé dans l'autre desdites première et deuxième transmissions de rotation, de manière à pouvoir tourner autour d'un quatrième axe de rotation, et un deuxième frein moteur électrique, qui agit sur le deuxième arbre intermédiaire, en étant capable de modifier une vitesse de rotation de celui-ci, à la suite de commandes reçues des moyens de commande auxquels il est électriquement connecté. D'une manière préférentielle, le premier arbre intermédiaire et le deuxième arbre intermédiaire présentent, en l'absence des freins moteurs, des vitesses de rotation différentes, le frein moteur agissant sur l'arbre intermédiaire le plus rapide est un alternateur présentant des bobines, dont on fait varier une excitation pour obtenir un effet de frein variable, et produisant un courant électrique, et le frein moteur agissant sur l'arbre intermédiaire le plus lent est un moteur électrique, qui est alimenté par le courant électrique produit par ledit alternateur et qui permet d'obtenir un effet d'accélération variable. Cet agencement est particulièrement avantageux car il permet de récupérer l'énergie développée par le freinage du premier arbre intermédiaire et de s'en servir pour la mise en marche d'un moteur électrique qui accélère le deuxième arbre de vitesse, avec pour résultat une obtention plus efficace de l'effet recherché, c'est-à-dire une modification du rapport de vitesses. La variation continue de l'effet frein moteur s'obtient en faisant varier l'excitation des bobines de l'alternateur, cette variation étant produite par l'intermédiaire des moyens de commande, soit manuellement, soit par un ordinateur qui prendra en compte différentes données, comme par exemple la vitesse de l'arbre de sortie, la vitesse de rotation à l'entrée, la puissance de transmission demandée, d'une manière analogue à ce qui se passe dans une boîte de vitesse automatique. Toutefois, à la différence de cette dernière, les moyens de commande agiront à présent en continu et non pas par sauts à partir de certaines limites.According to one embodiment of the invention, the apparatus further comprises a second intermediate shaft arranged in the other of said first and second rotation transmissions, so as to be able to rotate around a fourth axis of rotation, and a second electric motor brake, which acts on the second intermediate shaft, being capable of modifying a speed of rotation thereof, following commands received from the control means to which it is electrically connected. Preferably, the first intermediate shaft and the second intermediate shaft have, in the absence of the engine brakes, different rotation speeds, the engine brake acting on the fastest intermediate shaft is an alternator having coils, which excitation is varied to obtain a variable brake effect, and producing an electric current, and the engine brake acting on the slowest intermediate shaft is an electric motor, which is supplied by the electric current produced by said alternator and which provides a variable acceleration effect. This arrangement is particularly advantageous because it makes it possible to recover the energy developed by the braking of the first intermediate shaft and to use it for starting an electric motor which accelerates the second speed shaft, resulting in a more effective obtaining of the desired effect, that is to say a modification of the speed ratio. The continuous variation of the engine brake effect is obtained by varying the excitation of the alternator coils, this variation being produced by means of the control means, either manually or by a computer which will take into account different data, such as the speed of the output shaft, the speed of rotation at the input, the requested transmission power, in a similar way to what happens in an automatic gearbox. However, unlike the latter, the control means will now act continuously and not by jumps from certain limits.
Suivant une forme de réalisation de l'invention, le premier train d'engrenages épicycloïdal comporte un arbre d'entrée agencé au moins partiellement dans le premier carter rotatif de manière à pouvoir tourner autour du premier axe de rotation et cet arbre d'entrée est relié au moteur d'entraînement et sert d'entrée motrice.According to one embodiment of the invention, the first planetary gear train comprises an input shaft arranged at least partially in the first rotary casing so as to be able to rotate around the first axis of rotation and this input shaft is connected to the drive motor and serves as a motor input.
Suivant une autre forme de réalisation de l'invention, l'appareil comporte un deuxième carter rotatif, qui est agencé de manière à pouvoir tourner autour d'un cinquième axe de rotation et dans lequel est logé le deuxième train d'engrenages épicycloïdal dudit double train, qui permet une transmission de rotation à l'arbre de sortie, le premier train d'engrenages étant logé dans le premier carter rotatif. Ici, le double train d'engrenages épicycloïdal est divisé en deux trains séparés qui, chacun, sont logés dans un carter rotatif propre.According to another embodiment of the invention, the device comprises a second rotary casing, which is arranged so as to be able to rotate around a fifth axis of rotation and in which is housed the second planetary gear train of said double train, which allows a rotation transmission to the output shaft, the first gear train being housed in the first rotary casing. Here, the double planetary gear train is divided into two separate trains, each of which is housed in a clean rotating housing.
Suivant une forme de réalisation particulière de l'invention, le premier carter rotatif est agencé de manière à être entraîné en rotation par le moteur d'entraînement, en servant ainsi d'entrée motrice de l'appareil, et le double train d'engrenages est logé dans le premier carter rotatif. Dans une telle forme de réalisation, le double train d'engrenages est enfermé dans une seule enceinte et l'appareil se présente de manière relativement compacte.According to a particular embodiment of the invention, the first rotary casing is arranged so as to be driven in rotation by the drive motor, thus serving as the motor input of the device, and the double gear train is housed in the first rotary housing. In such an embodiment, the double gear train is enclosed in a single enclosure and the device is relatively compact.
D'autres formes de réalisation de l'appareil suivant l'invention sont indiquées dans les revendications annexées. D'autres détails et particularités de l'invention ressortiront de la description donnée ci-après, à titre non limitatif et avec référence aux dessins annexés.Other embodiments of the apparatus according to the invention are indicated in the appended claims. Other details and particularities of the invention will emerge from the description given below, without implied limitation and with reference to the attached drawings.
La figure 1 représente une forme de réalisation schématique, partiellement en coupe, d'un appareil suivant l'invention. La figure 2 représente d'une manière schématique une autre forme de réalisation d'appareil suivant l'invention.Figure 1 shows a schematic embodiment, partially in section, of an apparatus according to the invention. FIG. 2 schematically represents another embodiment of the apparatus according to the invention.
Sur les différents dessins, les éléments identiques ou analogues sont désignés par les mêmes références.In the various drawings, identical or analogous elements are designated by the same references.
Sur la figure 1, l'appareil de transmission représenté est agencé entre un moteur d'entraînement courant, non représenté, et couplé à un arbre d'entrée 1, et un dispositif récepteur entraînable courant, non représenté, et couplé à un arbre de sortie 2.In FIG. 1, the transmission device shown is arranged between a current drive motor, not shown, and coupled to an input shaft 1, and a current drivable receiving device, not shown, and coupled to a drive shaft exit 2.
L'appareil comprend un double train d'engrenages épicycloïdal qui présente un premier train d'engrenages épicycloïdal logé dans un premier carter rotatif 3 et un deuxième train d'engrenages épicycloïdal logé dans un deuxième carter rotatif 4. Chaque carter rotatif, avec son train d'engrenages, est un système connu que l'on peut trouver sur le marché par exemple sous la dénomination de système épicycloïdal REDEX (firme TEXROPE, Société Industrielle de Transmissions). Le premier train d'engrenages comprend un premier plateau porte-planétaire 5, monté sur l'arbre d'entrée 1 de manière à tourner avec lui, autour de son axe de rotation 6, et un deuxième plateau porte-planétaire 7, monté sur un arbre de sortie intercalaire 8 de manière à pouvoir tourner avec lui, autour de ce même axe de rotation 6. L'arbre d'entrée 1 fait partiellement saillie hors du carter 3, qui est coaxial à lui, et cela de manière à pouvoir tourner librement par rapport au carter. Dans l'exemple illustré cet arbre d'entrée 1 est creux et sert de guidage centré à l'arbre de sortie intercalaire 8, lui aussi coaxial à l'arbre d'entrée, et faisant partiellement aussi saillie hors du carter 3, de manière à pouvoir tourner librement par rapport à celui-ci.The apparatus comprises a double planetary gear train which has a first planetary gear train housed in a first rotary casing 3 and a second planetary gear train housed in a second rotary casing 4. Each rotary casing, with its train of gears, is a known system that can be found on the market for example under the name of the REDEX epicyclic system (firm TEXROPE, Société Industrielle de Transmissions). The first gear train comprises a first planetary carrier plate 5, mounted on the input shaft 1 so as to rotate with it, about its axis of rotation 6, and a second planetary carrier plate 7, mounted on an intermediate output shaft 8 so as to be able to rotate with it, around this same axis of rotation 6. The input shaft 1 partially protrudes from the casing 3, which is coaxial with it, and this so as to be able to rotate freely relative to the casing. In the example illustrated, this input shaft 1 is hollow and serves as a guide centered on the intermediate output shaft 8, which is also coaxial with the input shaft, and also partially protruding from the casing 3, so to be able to rotate freely in relation to it.
Dans le carter 3 illustré sur la figure 1 , plusieurs axes de pivotement 9 sont supportés parallèlement à l'axe de rotation 6, de manière à pouvoir tourner librement sur eux-mêmes, mais de façon à être entraînés en révolution autour de l'axe de rotation 6, lorsque le carter 3 effectue une rotation. Chaque axe de pivotement 9 porte deux satellites 10 et 11 de manière qu'ils tournent conjointement avec cet axe de pivotement. Chaque satellite 10 et 11 est en prise avec un des plateaux porte-planétaire 5 et 7. Le carter rotatif 3 présente enfin un système de prise, par exemple une denture externe 12 représentée de manière schématique, qui peut entrer en prise avec une transmission de rotation extérieure.In the casing 3 illustrated in FIG. 1, several pivot axes 9 are supported parallel to the axis of rotation 6, so as to be able to rotate freely on themselves, but so as to be driven in revolution around the axis of rotation 6, when the casing 3 rotates. Each pivot axis 9 carries two satellites 10 and 11 so that they rotate together with this pivot axis. Each satellite 10 and 11 is engaged with one of the planetary carrier plates 5 and 7. The rotary casing 3 finally has a engagement system, for example an external toothing 12 shown diagrammatically, which can engage with a transmission of external rotation.
Les diamètres du carter 3, des plateaux porte-planétaire 5 et 7, et des satellites 10 et 11 sont choisis de façon à établir entre l'arbre d'entrée 1 et l'arbre de sortie intercalaire 8 un rapport de transmission présélectionné (lequel pourra être modifié suivant l'invention comme décrit dans la suite).The diameters of the casing 3, of the planetary carrier plates 5 and 7, and of the satellites 10 and 11 are chosen so as to establish between the input shaft 1 and the intermediate output shaft 8 a preselected transmission ratio (which may be modified according to the invention as described below).
Le deuxième train d'engrenages comprend un troisième plateau porte-planétaire 13, monté sur un arbre d'entrée intercalaire 14, de manière à tourner autour de son axe de rotation. Dans l'exemple de réalisation illustré, cet axe de rotation est coaxial à l'axe de rotation 6. Le deuxième train d'engrenages comprend en outre un quatrième plateau porte-planétaire 15 monté sur l'arbre de sortie 2 de manière à pouvoir tourner avec lui, cet arbre de sortie étant à nouveau dans l'exemple de la figure 1 coaxial à l'axe de rotation 6 et faisant partiellement saillie hors du carter 4.The second gear train comprises a third planetary carrier plate 13, mounted on an intermediate input shaft 14, so as to rotate around its axis of rotation. In the illustrated embodiment, this axis of rotation is coaxial with the axis of rotation 6. The second gear train further comprises a fourth planetary carrier plate 15 mounted on the output shaft 2 so as to be able to turn with it, this output shaft being again in the example of the Figure 1 coaxial with the axis of rotation 6 and partially projecting from the casing 4.
L'arbre de sortie 2 est agencé de manière à pouvoir tourner librement par rapport au carter 4 et, dans cet exemple, il est prévu creux pour servir de guidage centré à l'arbre d'entrée intercalaire 14, qui lui aussi fait partiellement saillie hors du carter 4, de manière à pouvoir tourner librement par rapport à lui.The output shaft 2 is arranged so that it can rotate freely relative to the casing 4 and, in this example, it is provided hollow to serve as a guide centered on the intermediate input shaft 14, which also protrudes partially therefrom out of the casing 4, so that it can rotate freely relative to it.
Dans le carter 4, illustré sur la figure 1 , plusieurs axes de pivotement 16 sont supportés parallèlement à l'axe de rotation 6, de manière à pouvoir tourner librement sur eux-mêmes, mais de façon à être entraînés en révolution autour de l'axe de rotation 6, lorsque le carter 4 effectue une rotation. Chaque axe de pivotement 16 porte deux satellites 17 et 18 de manière qu'ils tournent conjointement avec cet axe de pivotement 16. Chacun des satellites 17 et 18 est en prise avec un des plateaux porte-planétaire 13 et 15.In the casing 4, illustrated in FIG. 1, several pivot axes 16 are supported parallel to the axis of rotation 6, so as to be able to rotate freely on themselves, but so as to be driven in revolution around the axis of rotation 6, when the casing 4 rotates. Each pivot axis 16 carries two satellites 17 and 18 so that they rotate together with this pivot axis 16. Each of the satellites 17 and 18 is engaged with one of the planetary carrier plates 13 and 15.
Dans l'exemple de la figure 1 , le carter rotatif 4 présente un système de prise, par exemple une denture externe 19 représentée de manière schématique, qui peut entrer en prise avec une transmission de rotation extérieure. Les diamètres du carter 4, des plateaux porte-planétaire 13 et 15 et des satellites 17 et 18 sont choisis de façon à établir entre l'arbre d'entrée intercalaire 14 et l'arbre de sortie 2 un rapport de transmission présélectionné (lequel pourra être modifié suivant l'invention comme décrit dans la suite). De plus le double train d'engrenages épicycloïdal illustré doit être choisi de façon à établir un rapport de transmission donné entre la vitesse de rotation d'entrée et la vitesse de rotation de sortie.In the example of FIG. 1, the rotary casing 4 has an engagement system, for example an external toothing 19 shown diagrammatically, which can engage with an external rotation transmission. The diameters of the casing 4, of the planetary carrier plates 13 and 15 and of the satellites 17 and 18 are chosen so as to establish between the intermediate input shaft 14 and the output shaft 2 a preselected transmission ratio (which may be modified according to the invention as described below). In addition, the double planetary gear train illustrated must be chosen so as to establish a given transmission ratio between the input rotation speed and the output rotation speed.
Dans l'exemple illustré sur la figure 1, un premier arbre intermédiaire 20 est agencé parallèlement à l'axe de rotation 6, de manière à pouvoir tourner sur lui-même. Il porte deux pignons dentés 21 et 22 qui sont chacun capables, par un engrenage, d'entrer en prise avec la denture 12 du carter 3 et respectivement la denture 19 du carter 4. Cet agencement réalise ainsi une première transmission de rotation à une sortie intermédiaire du carter 3, transmission qui est engagée par ailleurs avec le carter 4.In the example illustrated in Figure 1, a first intermediate shaft 20 is arranged parallel to the axis of rotation 6, so as to be able to rotate on itself. He wears two toothed gears 21 and 22 which are each capable, by a gear, of engaging with the toothing 12 of the casing 3 and respectively the toothing 19 of the casing 4. This arrangement thus produces a first rotation transmission at an intermediate output of the casing 3, transmission which is also engaged with the casing 4.
Dans cet exemple également, l'arbre de sortie intercalaire 8 et l'arbre d'entrée intercalaire 14 forment ensemble, ou prévoient entre eux coaxialement, un arbre intermédiaire 23 qui réalise ainsi une deuxième transmission de rotation entre le premier train d'engrenages épicycloïdal et le deuxième, à une entrée intermédiaire de celui-ci.In this example also, the intermediate output shaft 8 and the intermediate input shaft 14 together form, or provide between them coaxially, an intermediate shaft 23 which thus performs a second rotation transmission between the first planetary gear train and the second, at an intermediate entrance to it.
Un premier frein moteur 24 est agencé de manière à pouvoir agir sur le premier arbre intermédiaire 20. Ce frein moteur peut être par exemple un alternateur courant, muni de bobines, qui est électriquement connecté à un centre de commande 25, par exemple un ordinateur qui intègre des données d'entrée, comme la puissance du moteur d'entraînement, la vitesse de rotation de l'arbre d'entrée, la vitesse de l'arbre de sortie, etc. et qui peut agir automatiquement sur le frein moteur 24 de façon que celui-ci soit libère l'arbre intermédiaire 20, soit le freine, ou encore éventuellement le bloque, en faisant varier l'excitation des bobines. En cas de freinage, l'énergie libérée est transformée par l'alternateur en courant électrique.A first engine brake 24 is arranged so as to be able to act on the first intermediate shaft 20. This engine brake can for example be a current alternator, provided with coils, which is electrically connected to a control center 25, for example a computer which integrates input data, such as the power of the drive motor, the rotation speed of the input shaft, the speed of the output shaft, etc. and which can act automatically on the motor brake 24 so that the latter releases the intermediate shaft 20, either the brake, or even possibly blocks it, by varying the excitation of the coils. When braking, the energy released is transformed by the alternator into electric current.
Un deuxième frein moteur 26 peut aussi être agencé de manière à pouvoir agir sur le deuxième arbre intermédiaire 23, par exemple par l'intermédiaire de pignons dentés représentés de manière schématique. Ce deuxième frein moteur peut être par exemple un moteur électrique qui est électriquement connecté au centre de commande 25, ainsi qu'au premier frein moteur 24, pour pouvoir être alimenté en courant au moins partiellement par celui-ci. Le centre de commande 25 peut agir automatiquement sur le frein moteur 26 de façon que celui-ci soit libère l'arbre intermédiaire 23, soit le freine, ou encore le bloque, en faisant varier l'alimentation en courant du moteur électrique. Celui-ci récupère l'énergie dégagée par le premier frein moteur.A second motor brake 26 can also be arranged so as to be able to act on the second intermediate shaft 23, for example by means of toothed gears shown schematically. This second motor brake can for example be an electric motor which is electrically connected to the control center 25, as well as to the first motor brake 24, in order to be able to be supplied with current at least partially by the latter. The control center 25 can act automatically on the engine brake 26 so that the latter releases the intermediate shaft 23, either the brake, or the blocks, by varying the current supply to the electric motor. This recovers the energy released by the first engine brake.
Cet agencement permet ainsi de séparer sur deux axes différents (les deux arbres intermédiaires) une vitesse d'entrée unique, et cela au moyen du premier train d'engrenages, qui forme ainsi un premier différentiel, de créer une interaction entre ces deux axes, par l'intermédiaire d'au moins un des freins moteurs, avant de remélanger les deux vitesses dans le deuxième train d'engrenages, qui forme ainsi un deuxième différentiel. Cette interaction permet de faire varier de manière continue le rapport entre la vitesse d'entrée et la vitesse de sortie. Cet effet est obtenu en particulier parce que les vitesses aux sorties d'un différentiel se modifient l'une par rapport à l'autre en fonction du couple résistant.This arrangement thus makes it possible to separate on two different axes (the two intermediate shafts) a single input speed, and this by means of the first gear train, which thus forms a first differential, to create an interaction between these two axes, by means of at least one of the engine brakes, before remixing the two gears in the second gear train, which thus forms a second differential. This interaction makes it possible to continuously vary the ratio between the input speed and the output speed. This effect is obtained in particular because the speeds at the outputs of a differential change relative to each other as a function of the resisting torque.
Si l'on applique à présent au système suivant l'invention la formule de Willis bien connue à laquelle obéissent les vitesses dans un différentiel, on obtient pour le premier différentiel :If we now apply to the system according to the invention the well-known Willis formula to which the speeds in a differential obey, we obtain for the first differential:
et pour le deuxième différentiel, où ω14 = ω8,and for the second differential, where ω 14 = ω 8 ,
Dans cette équation, ω représente la vitesse de rotation de l'élément indiqué en indice, et d représente le diamètre de l'élément indiqué en indice. Dans le cas où d7 = dΗ et d5 = 8 x d10 dans le premier différentiel, et où d15 = 0,25 x d18 et d13 = 0,5 x d17 dans le deuxième différentiel, on obtient une vitesse de sortie ω2 qui peut varier entre 16 fois la vitesse d'entrée ω, et -8/7 fois la vitesse d'entrée ω Le premier cas correspond à une marche avant surmultipliée et le second cas à une marche arrière.In this equation, ω represents the speed of rotation of the element indicated in subscript, and d represents the diameter of the element indicated in subscript. In the case where d 7 = d Η and d 5 = 8 xd 10 in the first differential, and where d 15 = 0.25 xd 18 and d 13 = 0.5 xd 17 in the second differential, we obtain a speed of exit ω 2 which can vary between 16 times the speed of entry ω, and -8 / 7 times the speed of entry ω The first case corresponds to a forward drive and the second case to a reverse.
Dans le premier cas, l'arbre intermédiaire 20 est bloqué par le frein moteur 24 et l'arbre intermédiaire 23 est libre. Dans le second cas l'arbre intermédiaire 23 est bloqué par le frein moteur 26 et l'arbre intermédiaire 20 est libéré et tourne dans le sens inverse. La variation entre ces deux limites est continue par le jeu de freins moteurs qui agissent sur les arbres intermédiaires.In the first case, the intermediate shaft 20 is blocked by the engine brake 24 and the intermediate shaft 23 is free. In the second case, the intermediate shaft 23 is blocked by the engine brake 26 and the intermediate shaft 20 is released and rotates in the opposite direction. The variation between these two limits is continuous by the set of engine brakes which act on the intermediate shafts.
Dans la pratique, il sera préférable de choisir les rapports ω ω2 plus grands que dans cet exemple théorique, de façon que les positions extrêmes ne soient jamais atteintes.In practice, it will be preferable to choose the ratios ω ω 2 larger than in this theoretical example, so that the extreme positions are never reached.
Si dans l'exemple de réalisation illustré sur la figure 1 , les axes de rotation du carter 3, du carter 4, de l'arbre d'entrée 1 , de l'arbre de sortie 2, de l'arbre de sortie intercalaire 8 et de l'arbre d'entrée intercalaire 14 sont coaxiaux, il est possible de prévoir que certains d'entre eux ne le soient pas. Il est possible par exemple que la transmission de rotation entre l'arbre de sortie intercalaire 8 et l'arbre d'entrée intercalaire 14 forment un ou plusieurs angles de renvoi. Il en est de même pour la transmission de rotation entre le carter 3 et le carter 4.If in the embodiment illustrated in FIG. 1, the axes of rotation of the casing 3, of the casing 4, of the input shaft 1, of the output shaft 2, of the intermediate output shaft 8 and the intermediate input shaft 14 are coaxial, it is possible to provide that some of them are not. It is possible for example that the rotation transmission between the intermediate output shaft 8 and the intermediate input shaft 14 form one or more return angles. The same is true for the transmission of rotation between the housing 3 and the housing 4.
Dans la forme de réalisation illustrée sur la figure 2, le carter rotatif 27 est unique et le double train d'engrenages épicycloïdal est complètement logé à l'intérieur de celui-ci. C'est avec le carter rotatifIn the embodiment illustrated in FIG. 2, the rotary casing 27 is unique and the double planetary gear train is completely housed inside it. It is with the rotary housing
27 que le moteur d'entraînement est en prise, par sa denture externe 28.27 that the drive motor is engaged, by its external toothing 28.
Le carter rotatif sert donc ici d'entrée motrice.The rotary casing therefore serves here as a drive input.
Le double train d'engrenages est formé de deux trains fusionnés l'un dans l'autre. Le premier train d'engrenages comprend un plateau porte- planétaire 29 monté sur un arbre intercalaire de sortie 30, de manière à tourner avec lui, un plateau central 31 monté sur l'arbre de sortie 32 de manière à tourner avec lui et des satellites 33 et 34 agencés entre le plateau porte-planétaire 29 et respectivement le plateau central 31 , sur plusieurs axes de pivotement 41 parallèles à l'axe de rotation 6 du carter. Les satellites sont entraînés en révolution autour de cet axe lorsque le carter 27 effectue une rotation. Chaque axe de pivotement 41 porte deux satellites 33 et 34 qui sont chacun en prise avec le plateau porte- planétaire 29 ou le plateau central 31.The double gear train consists of two trains merged into each other. The first gear train comprises a planetary carrier plate 29 mounted on an output intermediate shaft 30, so as to rotate with it, a central plate 31 mounted on the output shaft 32 so as to rotate with it and satellites 33 and 34 arranged between the planetary carrier plate 29 and respectively the central plate 31, on several pivot axes 41 parallel to the axis of rotation 6 of the casing. The satellites are driven in revolution around this axis when the casing 27 rotates. Each pivot axis 41 carries two satellites 33 and 34 which are each engaged with the planetary carrier plate 29 or the central plate 31.
Le deuxième train d'engrenages comprend un plateau porte-planétaire 35, monté sur un arbre d'entrée intercalaire 36, de manière à tourner autour de son axe de rotation, et le plateau central 31 prédécrit. Il comporte également des satellites, le satellite 37 et le satellite 34 prédécrit. Les satellites 37 sont chacun agencés, comme les satellites 33 et 34, sur un axe de pivotement 41.The second gear train comprises a planetary carrier plate 35, mounted on an intermediate input shaft 36, so as to rotate about its axis of rotation, and the central plate 31 described above. It also includes satellites, satellite 37 and satellite 34 described above. The satellites 37 are each arranged, like the satellites 33 and 34, on a pivot axis 41.
La première transmission de rotation comprend l'arbre de sortie intercalaire 30 à titre de premier arbre intermédiaire sur lequel agit le frein moteur 38 par un jeu d'engrenages. La deuxième transmission de rotation comprend l'arbre d'entrée intercalaire 36 à titre de deuxième arbre intermédiaire sur lequel agit le frein moteur 39. Les deux freins moteurs sont électriquement connectés au centre de commande 40 et mutuellement entre eux.The first rotation transmission comprises the intermediate output shaft 30 as the first intermediate shaft on which the engine brake 38 acts by a set of gears. The second rotation transmission comprises the intermediate input shaft 36 as the second intermediate shaft on which the engine brake 39 acts. The two engine brakes are electrically connected to the control center 40 and to each other.
Comme on peut le constater, dans l'exemple de la figure 2, les axes de rotation du carter 27, de l'arbre de sortie 32, de l'arbre de sortie intercalaire 30 et de l'arbre d'entrée intercalaire 36, sont coaxiaux.As can be seen, in the example of FIG. 2, the axes of rotation of the casing 27, the output shaft 32, the intermediate output shaft 30 and the intermediate input shaft 36, are coaxial.
Cette forme de réalisation présente l'avantage d'un moindre encombrement.This embodiment has the advantage of less bulk.
D'une manière générale, les avantages des appareils de transmission suivant l'invention sont entre autres les suivants : - ils permettent de faire tourner tout moteur en permanence à son meilleur rendement pour la puissance demandée, ce qui entraîne une consommation minimum,In general, the advantages of the transmission devices according to the invention are inter alia the following: - they make it possible to run any motor permanently at its best efficiency for the requested power, which leads to minimum consumption,
- ils font donner au moteur sa puissance maximum dès le démarrage ou à n'importe quel moment,- they cause the engine to give its maximum power from start-up or at any time,
- ils permettent d'obtenir une vitesse de sortie maximum à la puissance maximum, en choisissant la vitesse d'entrée qui sera préférable pour le moteur dans ces conditions,- they make it possible to obtain a maximum output speed at maximum power, by choosing the input speed which will be preferable for the engine under these conditions,
- ils diminuent la pollution, car le moteur tourne toujours à son rendement maximum,- they reduce pollution, because the engine always runs at its maximum efficiency,
- ils permettent une accélération très rapide.- they allow very rapid acceleration.
Le rendement de l'appareil de transmission proprement dit est très élevé et comparable à celui des boîtes de vitesse mécaniques existantes, la transmission de puissance du moteur d'entraînement au dispositif récepteur entraînable se faisant au moyen d'engrenages comme dans le cas des boîtes de vitesses mécaniques.The efficiency of the transmission device itself is very high and comparable to that of existing mechanical gearboxes, the transmission of power from the drive motor to the drive receiver device being done by means of gears as in the case of the boxes. mechanical speeds.
Il doit être entendu que la présente invention n'est en aucune façon limitée aux formes de réalisation décrites ci-dessus et que bien des modifications peuvent y être apportées dans le cadre des revendications annexées. It should be understood that the present invention is in no way limited to the embodiments described above and that many modifications can be made thereto within the scope of the appended claims.

Claims

REVENDICATIONS
1. Appareil de transmission de vitesses, agencé entre un moteur d'entraînement et un dispositif récepteur entraînable, comprenant un premier carter rotatif (3, 27) agencé de manière à pouvoir tourner autour d'un premier axe de rotation (6), un double train d'engrenages épicycloïdal qui comprend un premier train et un deuxième train et qui est agencé au moins partiellement dans ledit premier carter rotatif (3, 27), entre une entrée motrice reliée au moteur d'entraînement et un arbre de sortie (2, 32), agencé de manière à pouvoir tourner autour d'un deuxième axe de rotation et relié au dispositif récepteur entraînable, le double train susdit établissant entre l'entrée motrice et l'arbre de sortie (2, 32) un rapport de transmission entre une vitesse de rotation d'entrée et une vitesse de rotation de sortie, une première transmission de rotation (12, 20, 21; 30) agencée à une sortie intermédiaire du premier train d'engrenages épicycloïdal, une deuxième transmission de rotation (14; 36) agencée à une entrée intermédiaire du deuxième train d'engrenages épicycloïdal, un premier arbre intermédiaire (20; 30) agencé dans l'une desdites première et deuxième transmission de rotation, de manière à pouvoir tourner autour d'un troisième axe de rotation, un premier frein moteur électrique (24; 38) agissant sur le premier arbre intermédiaire (20; 30) et capable de modifier une vitesse de rotation de celui-ci, et des moyens de commande (25; 40) électriquement connectés au premier frein moteur (24; 38) et commandant celui-ci de façon à pouvoir modifier de manière continue la vitesse de rotation du premier arbre intermédiaire (20; 30) et donc le rapport de transmission entre ladite vitesse de rotation d'entrée et ladite vitesse de rotation de sortie. 1. A gear transmission apparatus, arranged between a drive motor and a drivable receiving device, comprising a first rotary casing (3, 27) arranged so as to be able to rotate around a first axis of rotation (6), a double planetary gear train which comprises a first train and a second train and which is arranged at least partially in said first rotary casing (3, 27), between a drive input connected to the drive motor and an output shaft (2 , 32), arranged so as to be able to rotate around a second axis of rotation and connected to the drive receiver device, the aforementioned double train establishing between the drive input and the output shaft (2, 32) a transmission ratio between an input rotation speed and an output rotation speed, a first rotation transmission (12, 20, 21; 30) arranged at an intermediate output of the first planetary gear train, a second transmission ission of rotation (14; 36) arranged at an intermediate input of the second planetary gear train, a first intermediate shaft (20; 30) arranged in one of said first and second rotation transmission, so as to be able to rotate about a third axis of rotation, a first electric motor brake (24; 38) acting on the first intermediate shaft (20; 30) and capable of modifying a speed of rotation thereof, and control means (25; 40) electrically connected to the first engine brake (24; 38) and controlling it so as to be able to continuously modify the speed of rotation of the first intermediate shaft (20; 30) and therefore the transmission ratio between said input rotation speed and said output rotation speed.
2. Appareil suivant la revendication 1, caractérisé en ce qu'il comprend en outre un deuxième arbre intermédiaire (23; 36) agencé dans l'autre desdites première et deuxième transmissions de rotation, de manière à pouvoir tourner autour d'un quatrième axe de rotation, et un deuxième frein moteur électrique (26; 39), qui agit sur le deuxième arbre intermédiaire (23; 36), en étant capable de modifier une vitesse de rotation de celui-ci, à la suite de commandes reçues des moyens de commande (25; 40) auxquels il est électriquement connecté.2. Apparatus according to claim 1, characterized in that it further comprises a second intermediate shaft (23; 36) arranged in the other of said first and second rotational transmissions, so as to be able to rotate around a fourth axis of rotation, and a second electric motor brake (26; 39), which acts on the second intermediate shaft (23; 36), being capable of modifying a speed of rotation thereof, following commands received from the means control (25; 40) to which it is electrically connected.
3. Appareil suivant la revendication 2, caractérisé en ce que le premier arbre intermédiaire (20; 30) et le deuxième arbre intermédiaire (23; 36) présentent, en l'absence des freins moteurs, des vitesses de rotation différentes, en ce que le frein moteur (24, 38) agissant sur l'arbre intermédiaire le plus rapide (20; 30) est un alternateur présentant des bobines, dont on fait varier une excitation pour obtenir un effet de frein variable, et produisant un courant électrique, et en ce que le frein moteur (26; 39) agissant sur l'arbre intermédiaire le plus lent (23; 36) est un moteur électrique, qui est alimenté par du courant électrique au moins partiellement produit par ledit alternateur et qui permet d'obtenir un effet d'accélération variable. 3. Apparatus according to claim 2, characterized in that the first intermediate shaft (20; 30) and the second intermediate shaft (23; 36) have, in the absence of the engine brakes, different rotational speeds, in that the engine brake (24, 38) acting on the fastest intermediate shaft (20; 30) is an alternator having coils, an excitation of which is varied to obtain a variable brake effect, and producing an electric current, and in that the engine brake (26; 39) acting on the slowest intermediate shaft (23; 36) is an electric motor, which is supplied with electric current at least partially produced by said alternator and which makes it possible to obtain a variable acceleration effect.
4. Appareil suivant l'une quelconque des revendications 1 à 3, caractérisé en ce que le premier train d'engrenages épicycloïdal comporte un arbre d'entrée (1) agencé au moins partiellement dans le premier carter rotatif (3) de manière à pouvoir tourner autour du premier axe de rotation (6) et en ce que cet arbre d'entrée (1) est relié au moteur d'entraînement et sert d'entrée motrice.4. Apparatus according to any one of claims 1 to 3, characterized in that the first planetary gear train comprises an input shaft (1) arranged at least partially in the first rotary casing (3) so as to be able rotate around the first axis of rotation (6) and in that this input shaft (1) is connected to the drive motor and serves as a motor input.
5. Appareil suivant la revendication 4, caractérisé en ce qu'il comporte un deuxième carter rotatif (4), qui est agencé de manière à pouvoir tourner autour d'un cinquième axe de rotation et dans lequel est logé le deuxième train d'engrenages épicycloïdal dudit double train, qui permet une transmission de rotation à l'arbre de sortie (2), le premier train d'engrenages étant logé dans le premier carter rotatif (3).5. Apparatus according to claim 4, characterized in that it comprises a second rotary casing (4), which is arranged so as to be able to rotate around a fifth axis of rotation and in which is housed the second gear train epicyclic of said double train, which allows a rotation transmission to the output shaft (2), the first gear train being housed in the first rotary casing (3).
6. Appareil suivant la revendication 5, caractérisé en ce ' que le premier train d'engrenages comprend un premier plateau porte- planétaire (5), monté sur l'arbre d'entrée (1) de manière à tourner avec lui, un deuxième plateau porte-planétaire (7) monté sur un arbre de sortie intercalaire (8) de manière à pouvoir tourner avec lui, et des premiers satellites (10, 11) agencés entre les premier et deuxième plateaux porte- planétaire (5, 7) de manière à pouvoir tourner avec au moins un premier axe de pivotement (9) qui est parallèle au premier axe de rotation (6) et qui effectue une révolution autour de celui-ci pendant une rotation du premier carter (3), en ce que le deuxième train d'engrenages comprend un troisième plateau porte-planétaire (13) monté sur un arbre d'entrée intercalaire (14), capable de tourner autour du deuxième axe de rotation, de manière à tourner avec lui, un quatrième plateau porte-planétaire (15) monté sur l'arbre de sortie (2) de manière à tourner avec lui, et des deuxièmes satellites (17, 18) agencés entre les troisième et quatrième plateaux porte-planétaires (13, 15) de manière à pouvoir tourner ensemble avec au moins un deuxième axe de pivotement (16) qui est parallèle au deuxième axe de rotation et qui effectue une révolution autour de celui-ci pendant une rotation du deuxième carter (4), en ce que ladite première transmission de rotation comprend un arbre de transmission, qui entre en prise par des jeux d'engrenages (12, 21, 19, 22) avec chacun des deux carters rotatifs (3, 4) et qui forme ledit premier arbre intermédiaire (20) sur lequel agit le premier frein moteur (24), et en ce que ladite deuxième transmission de rotation est agencée entre l'arbre de sortie intercalaire (8) du premier train d'engrenages et l'arbre d'entrée intercalaire (14) du deuxième train d'engrenages.6. Apparatus according to claim 5, characterized in that the first gear train comprises a first planetary carrier plate (5), mounted on the input shaft (1) so as to rotate with it, a second planetary carrier plate (7) mounted on an intermediate output shaft (8) so as to be able to rotate with it, and first satellites (10, 11) arranged between the first and second planetary carrier plates (5, 7) of so as to be able to rotate with at least a first pivot axis (9) which is parallel to the first axis of rotation (6) and which rotates around it during a rotation of the first casing (3), in that the second gear train comprises a third planetary carrier plate (13) mounted on an intermediate input shaft (14), capable of rotating around the second axis of rotation, so as to rotate with it, a fourth planetary carrier plate (15) mounted on the output shaft (2) so re to rotate with it, and second satellites (17, 18) arranged between the third and fourth planetary carrier plates (13, 15) so as to be able to rotate together with at least one second pivot axis (16) which is parallel to the second axis of rotation and which performs a revolution around it during a rotation of the second casing (4), in that said first rotation transmission comprises a transmission shaft, which engages by sets of gears ( 12, 21, 19, 22) with each of the two rotary casings (3, 4) and which forms said first intermediate shaft (20) on which the first engine brake (24) acts, and in that said second rotation transmission is arranged between the intermediate output shaft (8) of the first gear train and the intermediate input shaft (14) of the second gear train.
7. Appareil suivant la revendication 6, caractérisé en ce que l'arbre de sortie intercalaire (8) et l'arbre d'entrée intercalaire (14) forment ensemble un deuxième arbre intermédiaire (23) sur lequel agit un deuxième frein moteur (26).7. Apparatus according to claim 6, characterized in that the intermediate output shaft (8) and the intermediate input shaft (14) together form a second intermediate shaft (23) on which a second engine brake (26) acts.
8. Appareil suivant l'une quelconque des revendications 5 à 7, caractérisé en ce que les premier et deuxième axes de rotation sont coaxiaux, ainsi que les quatrième et cinquième axes de rotation, tous ces axes pouvant en outre être simultanément coaxiaux.8. Apparatus according to any one of claims 5 to 7, characterized in that the first and second axes of rotation are coaxial, as well as the fourth and fifth axes of rotation, all these axes can also be simultaneously coaxial.
9. Appareil suivant l'une quelconque des revendications 2 et 3, caractérisé en ce que le premier carter rotatif (27) est agencé de manière à être entraîné en rotation par le moteur d'entraînement, en servant ainsi d'entrée motrice de l'appareil, et en ce que le double train d'engrenages est logé dans le premier carter rotatif (27).9. Apparatus according to any one of claims 2 and 3, characterized in that the first rotary casing (27) is arranged so as to be driven in rotation by the drive motor, thus serving as the motor input of the 'apparatus, and in that the double gear train is housed in the first rotary housing (27).
10. Appareil suivant la revendication 9, caractérisé en ce que le premier train d'engrenages comprend un premier plateau porte- planétaire (29) monté sur un arbre intercalaire de sortie (30), de manière à tourner avec lui, un plateau central (31) monté sur l'arbre de sortie (32) de manière à tourner avec lui, et des premiers satellites (33, 34) agencés entre le premier plateau porte-planétaire (29) et le plateau central (31) de manière à pouvoir tourner ensemble avec au moins un axe de pivotement (41) qui est parallèle au premier axe de rotation (6) et qui effectue une révolution autour de celui-ci pendant une rotation du premier carter (27), en ce que le deuxième train d'engrenages comprend un deuxième plateau porte-planétaire (35) monté sur un deuxième arbre intercalaire d'entrée (36), ledit plateau central (31) monté sur l'arbre de sortie (32), et des deuxièmes satellites (34, 37) agencés entre le deuxième plateau porte-planétaire (35) et le plateau central (31) de manière à pouvoir tourner ensemble et avec les premiers satellites (33, 34) et ledit au moins un axe de pivotement (41), en ce que ladite première transmission de rotation de rotation comprend l'arbre de sortie intercalaire (30) à titre de premier arbre intermédiaire sur lequel agit ledit premier frein moteur (38), et en ce que ladite deuxième transmission comprend l'arbre d'entrée intercalaire (36) à titre de deuxième arbre intermédiaire sur lequel agit ledit deuxième frein moteur (39).10. Apparatus according to claim 9, characterized in that the first gear train comprises a first planetary carrier plate (29) mounted on an intermediate output shaft (30), so as to rotate with it, a central plate ( 31) mounted on the output shaft (32) so as to rotate with it, and first satellites (33, 34) arranged between the first planetary carrier plate (29) and the central plate (31) so as to be able rotate together with at least one pivot axis (41) which is parallel to the first axis of rotation (6) and which rotates around it during a rotation of the first casing (27), in that the second train d gears comprises a second planetary carrier plate (35) mounted on a second input intermediate shaft (36), said central plate (31) mounted on the output shaft (32), and second satellites (34, 37 ) arranged between the second planetary carrier plate (35) and the central plate (31) so as to be able to rotate together and with the first satellites (33, 34) and said at least one pivot axis (41), in that said first rotation rotation transmission comprises the intermediate output shaft (30 ) as the first intermediate shaft on which said first engine brake (38) acts, and in that said second transmission comprises the intermediate input shaft (36) as a second intermediate shaft on which said second engine brake (39) acts.
11. Appareil suivant l'une ou l'autre des revendications 9 et 10, caractérisé en ce que lesdits premier, deuxième, troisième et quatrième axes de rotation sont coaxiaux.11. Apparatus according to either of claims 9 and 10, characterized in that said first, second, third and fourth axes of rotation are coaxial.
12. Appareil suivant l'une quelconque des revendications 1 à 11, caractérisé en ce que les moyens de commande (25, 40) sont un ordinateur capable d'intégrer des données d'entrée et de transmettre des commandes correspondantes au premier frein moteur ainsi qu'à un éventuel deuxième frein moteur. 12. Apparatus according to any one of claims 1 to 11, characterized in that the control means (25, 40) are a computer capable of integrating input data and of transmitting corresponding commands to the first engine brake as well than a possible second engine brake.
EP02748476A 2001-07-04 2002-07-03 Speed transmission apparatus Withdrawn EP1402202A1 (en)

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BE200100451 2001-07-04
BE2001/0451A BE1014275A3 (en) 2001-07-04 2001-07-04 Speed transmission device.
PCT/BE2002/000112 WO2003004905A1 (en) 2001-07-04 2002-07-03 Speed transmission apparatus

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US7037230B2 (en) 2006-05-02
US20040166979A1 (en) 2004-08-26
BE1014275A3 (en) 2003-07-01

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